Seat reclining apparatus

ABSTRACT

A seat reclining apparatus includes a base plate, a ratchet plate, a lock member guided by a guide groove of the base plate between engaged and disengaged positions, a first cam between the base plate and the ratchet plate, and a second cam which moves toward and presses the lock member to an engaged position by the first cam when the first cam rotates from the unlocked to locked positions. The second cam includes a surface contact portion which comes in surface contact with a guide surface in the guide groove, an engaging portion which is pressed by the first cam, and a pressing portion which presses a pressed portion of the lock member. One and the other of the pressing portion and the pressed portion respectively includes a flat surface and a curved surface that is convex toward the flat surface.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a seat reclining apparatus for adjustment of the seatback angle of a reclining seat.

2. Description of Related Art

Japanese Unexamined Patent Publication No. 2012-51466 discloses a known seat reclining apparatus which includes a base plate which is fixed to a seat cushion side frame, a ratchet plate (ratchet) which is fixed to a seatback side frame and provided on the inner periphery thereof with an annular internal gear, a rotational center shaft for the base plate and the ratchet plate, a plurality (three) of lock members (pawls) which are supported to be movable relative to the base plate in radial directions of the rotational center shaft, a first cam (rotational cam) which rotates with the rotational center shaft, a plurality (three) of columnar second cams (circular cams) which are installed to be movable between the lock members and the first cam, respectively, and a lock spring (spiral spring) which biases the first cam to rotate the first cam.

A plurality (three) of guide grooves are recessed on a surface of the base plate which faces the ratchet plate to extend linearly toward the outer periphery of the base plate from the center side thereof. Each of the three guide grooves is provided on both sides (both side walls) therein with a pair of flat guide surfaces, respectively, which are parallel to each other.

An outer toothed portion is formed on an outer peripheral surface of each lock member. Each lock member is installed in the associated guide groove and guided thereby so as to be movable relative to the base plate (the associated guide groove) between an engaged position in which the outer toothed portion is engaged with the internal gear of the ratchet plate and a disengaged position in which the outer toothed portion is disengaged radially inwards from the internal gear of the ratchet plate.

The first cam is rotatable between a locked position to position each lock member in the engaged position and an unlocked position to position each lock member in the disengaged position. The lock spring biases the first cam toward the locked position.

When an operating lever (hand-operated lever) which is linked with the rotational center shaft is not manually rotated, the first cam rotates toward the locked position by the rotational biasing force of the lock spring, which causes each lock member to move toward the engaged position. In addition, the rotation of the first cam toward the locked position causes the first cam to press each second cam, and subsequently, each second cam pressed by the first cam comes into contact with and presses the associated lock member toward the engaged position. This causes the outer toothed portion of each lock member to be engaged with the internal gear of the ratchet plate, and consequently, the seatback side frame (seatback) becomes non-rotatable (temporarily fixed) relative to the seat cushion side frame (seat cushion).

On the other hand, the operating lever is manually rotated against the rotational biasing force of the lock spring, the first cam moves to the unlocked position. Thereupon, the pressing force exerted on the three lock members from the three second cams is canceled, and each lock member having moved to the engaged position moves toward the disengaged position, which causes the outer toothed portion of each lock member to be disengaged from the internal gear of the ratchet plate. As a result, the seatback side frame (seatback) becomes rotatable relative to the seat cushion side frame (seat cushion).

Each second cam of the seat reclining apparatus disclosed in the above-mentioned Japanese Unexamined Patent Publication No. 2012-51466 is contactable not only with the first cam and each lock member but also with one of the pair of flat guide surfaces of the associated guide groove.

However, the portion of each second cam which comes in contact with one of the pair of guide surfaces of the associated guide groove is a curved surface (circular arc surface), thus coming in line contact with this one guide surface, so that concentrated loads easily occur at the contact portion therebetween.

Therefore, when the seat reclining apparatus is in a locked state, if a vehicle which incorporates the seat reclining apparatus collides with another vehicle or object and this collision causes the seatback to rotate forward or rearward vigorously, there is a possibility of large concentrated loads occurring at the aforementioned line-contact portion.

To overcome this drawback, for instance, the shape of the second cam(s) can be formed into the shape that is shown in a comparative example (not known in the art) of the seat reclining apparatus shown in FIG. 27.

The second cam in this comparative example (only one second cam is shown in FIG. 27) includes a slide-contact flat surface which comes in surface contact with one of the pair of guide surfaces of the associated guide groove and a flat pressing portion which can come into surface contact with a flat pressed portion formed on the associated lock member.

In this comparative example, since each second cam includes the slide-contact flat surface (which comes in surface contact with the one guide surface of the associated guide groove), the possibility of concentrated loads occurring between each second cam and the associated guide surface is small.

However, since each second cam in the example shown in FIG. 27 includes, in addition to the slide-contact flat surface, the flat pressing portion, which can come into surface contact with the pressed portion of the associated lock member, if an error occurs between the shape of each second cam and the design shape thereof, each second cam may become positionally unstable when the first cam rotates, so that the operation of each second cam may become unsmooth.

SUMMARY OF THE INVENTION

The present invention provides a seat reclining apparatus in which a second cam, provided separately from a first cam for moving a lock member, for pressing the lock member in a locking direction does not easily cause concentrated loads between the second cam and a guide groove of the base plate which guides the lock member; moreover, the possibility of the operation of the seat reclining apparatus becoming unsmooth when the first cam rotates is small.

According to an aspect of the present invention, a seat reclining apparatus is provided, including a base plate which is fixed to one of a seat cushion side frame and a seatback side frame; a ratchet plate which includes an internal gear, the ratchet plate being fixed to the other of the seat cushion side frame and the seatback side frame so as to face the base plate while being rotatable relative thereto; a guide groove which is formed on a surface of the base plate which faces the ratchet plate; a lock member guided by the guide groove so as to be movable between an engaged position, in which an outer toothed portion formed on an outer peripheral surface of the lock member is engaged with the internal gear of the ratchet plate, and a disengaged position, in which the outer toothed portion is disengaged from the internal gear of the ratchet plate toward an inner peripheral side; a first cam which is positioned between the base plate and the ratchet plate and rotates relative to the base plate and the ratchet plate in association with an operation of operating member between a locked position to position the lock member in the engaged position and an unlocked position to position the lock member in the disengaged position; and a second cam which moves toward the lock member and presses the lock member to the engaged position by receiving a force from the first cam when the first cam rotates from the unlocked position to the locked position. The second cam includes a surface contact portion which comes in surface contact with a guide surface in the guide groove, an engaging portion which is pressed by the first cam, and a pressing portion which presses a pressed portion of the lock member. One of the pressing portion of the second cam and the pressed portion of the lock member includes a flat surface, and the other of the pressing portion of the second cam and the pressed portion of the lock member includes a curved surface that is convex toward the flat surface.

Since the second cam according to the present invention is provided with the surface contact portion, which comes in surface contact with the guide groove of the base plate, concentrated loads do not easily occur between the guide groove (the base plate) and the second cam.

In addition, one of the pressing portion of the second cam and the pressed portion of the lock member is a flat surface and the other a curved surface which is convex toward the aforementioned flat surface. Therefore, even if an error exists between the shape of the second cam (the pressing portion) and the design shape thereof, the possibility of the second cam becoming positionally unstable when the first cam rotates is small, so that the operation of the second cam does not easily become unsmooth.

It is desirable for the engaging portion of the second cam to include a curved surface that is convex toward the first cam, and for the curvature of the curved surface of the engaging portion of the second cam to be greater than the curvature of the curved surface of the other of the pressing portion of the second cam and the pressed portion of the lock member. Accordingly, the curved surface, which constitutes one of the pressing portion of the second cam and the pressed portion of the lock member becomes almost flat in shape. Therefore, one of the pressing portion of the second cam and the pressed portion of the lock member easily deforms plastically into the same shape as the other when the pressing portion of the second cam and the pressed portion of the lock member come into contact with each other with a large force due to, e.g., a collision of a vehicle which incorporates the seat reclining apparatus with another vehicle. If the pressing portion of the second cam and the pressed portion of the lock member are formed to be mutually identical in shape, the pressing portion of the second cam and the pressed portion of the lock member come in surface contact with each other, which reduces the possibility of large concentrated loads occurring therebetween. Accordingly, one or both of the second cam and the lock member can be prevented from being deformed or damaged in an efficient manner.

It is desirable for the pressing portion of the second cam and the pressed portion of the lock member to include the flat surface and the curved surface, respectively. The surface contact portion of the second cam comprises a flat surface. The second cam is symmetrical in shape with respect to a straight line passing between the surface contact portion and the pressing portion. Accordingly, in the case where a vehicle seat is provided with left and right seat reclining apparatuses on both sides (left and right sides) thereof (along with left and right seat cushion side frames and left and right seatback side frames), respectively, common second cams can be applied to the left and right seat reclining apparatuses.

It is desirable for the guide groove to include a plurality of guide grooves, and for the lock member to include a plurality of lock members which are guided by the plurality of guide grooves, respectively. The second cam operates in association with one of the plurality of lock members.

The present disclosure relates to subject matter contained in Japanese Patent Application No. 2012-204639 (filed on Sep. 18, 2012) which is expressly incorporated herein by reference in its entirety.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will be discussed below in detail with reference to the accompanying drawings, in which:

FIG. 1 is a side elevational view of a vehicle seat to which an embodiment of a seat reclining apparatus according to the present invention has been applied;

FIG. 2 is an exploded perspective view of the seat reclining apparatus;

FIG. 3 is a left-side elevational view of the seat reclining apparatus;

FIG. 4 is a right-side elevational view of the seat reclining apparatus;

FIG. 5 is a rear elevational view of the seat reclining apparatus;

FIG. 6 is a right-side elevational view of the seat reclining apparatus in a locked state and a seat cushion side frame;

FIG. 7 is a left-side elevational view of the seat reclining apparatus in a locked state and a seat cushion side frame;

FIG. 8 is a cross sectional view taken along the line VIII-VIII shown in FIG. 6, viewed in the direction of the appended arrows;

FIG. 9 is a cross sectional view taken along the line IX-IX shown in FIG. 6, viewed in the direction of the appended arrows;

FIG. 10 is a cross sectional view taken along the line X-X shown in FIG. 6, viewed in the direction of the appended arrows;

FIG. 11 is an enlarged view of a portion of the seat reclining apparatus which is designated by the Roman numeral XI shown in FIG. 6;

FIG. 12 is a cross sectional view taken along the line XII-XII shown in FIG. 7, viewed in the direction of the appended arrows;

FIG. 13 is an external side (right-side) elevational view of a base plate shown in FIG. 2, etc.;

FIG. 14 is an enlarged side view of a portion of the base plate and a lock spring shown in FIG. 2, etc.;

FIG. 15 is an enlarged side view of a spring cover shown in FIG. 2, etc.;

FIG. 16 shows the spring cover, viewed in the direction of the arrow XVI shown in FIG. 15;

FIG. 17 is a cross sectional view taken along the line XVII-XVII shown in FIG. 15, viewed in the direction of the appended arrows;

FIG. 18 is a right-side elevational view of a rotational center shaft shown in FIG. 2, etc.;

FIG. 19 is a cross sectional view taken along the line XIX-XIX shown in FIG. 18, viewed in the direction of the appended arrows;

FIG. 20 is a left-side elevational view of a rotational cam (first cam) shown in FIG. 2, etc.;

FIG. 21 is a cross sectional view taken along the line XXI-XXI shown in FIG. 8, viewed in the direction of the appended arrows, from which the seat cushion side frame, a retaining ring, anti-rotation pins and an annular flange are removed for clarity;

FIG. 22 is a view similar to that of FIG. 21, showing the seat reclining apparatus in an unlocked state from which two lock members are further removed for clarity;

FIG. 23 is a view similar to that of FIG. 21, showing the seat reclining apparatus in an unlocked holding state;

FIG. 24 is an enlarged view of a portion of the seat reclining apparatus which is designated by the Roman numeral XI shown in FIG. 22;

FIG. 25 is an enlarged view of a wedge shown in FIG. 2, etc.;

FIG. 26 is a view similar to that of FIG. 24, illustrating a modified embodiment of the seat reclining apparatus; and

FIG. 27 is a view similar to that of FIG. 24, illustrating a comparative example of seat reclining apparatus.

DESCRIPTION OF THE EMBODIMENTS

An embodiment of the present invention will be hereinafter discussed with reference to FIGS. 1 through 25. Directions described in the following description are defined based on the directions of arrows shown in the drawings. In the following description, the term “inner peripheral side” refers to the center side of a base plate 27 of the seat reclining apparatus 25 and the term “outer peripheral side” refers to the radially opposite side of the base plate 27 from the center side thereof.

A vehicle seat 10 shown in FIG. 1 is a right-side seat and is provided with a seat cushion 11 which is supported by a vehicle interior floor of a vehicle (e.g., an automobile) via a seat rail, and a seatback 12 which is rotatable relative to (pivoted at) the rear of the seat cushion 11. A pair of left and right seat cushion frames, made of metal, are installed inside the seat cushion 11 in a fixed state. Each seat cushion frame is a plate-shaped member extending in the forward/rearward direction (horizontal direction with respect to FIG. 1), and the rear end of each seat cushion frame includes a rear frame (seat cushion side frame) 13 (see FIG. 2, etc.), made of metal, which projects upward. The rear frame 13 is provided with a seat-cushion-side connecting hole 14 formed as a circular through-hole with three engaging holes 15 formed at intervals of 120 degrees (i.e. at equi-angular intervals) at the circumference thereof. The three engaging holes 15 are formed in such a manner to be recessed radially outwards from the circumference of the seat-cushion-side connecting hole 14. Each engaging hole 15 is substantially rectangular in shape, and both ends of each engaging hole 15 in the lengthwise direction thereof (circumferential direction about the center of the seat-cushion-side connecting hole 14) are formed by two flat portions 15 a which are parallel to each other. The vehicle seat 10 is provided inside the seatback 12 with a pair of left and right seatback side frames 16 (only a lower part of the right seatback side frame 16 is shown by two-dot chain lines in FIG. 2) made of metal which are installed in a fixed state (see FIG. 2). Each seatback side frame 16 is a plate-shaped member extending in the lengthwise direction of the seatback 12. Each seatback side frame 16 is provided, in a lower portion thereof (which becomes a rear portion thereof when the seatback 12 is tilted forward), with a seatback-side connecting hole 17 formed as a through-hole which includes a substantially square-shaped hole and a total of four fitting holes 18 which are respectively formed on the four sides of the aforementioned square-shaped hole. Each fitting hole 18 is substantially rectangular in shape.

The left and right rear frames 13 are installed in the internal space of the seatback 12. The left and right seatback side frames 16 are positioned in between the left and right rear frames 13. The left seatback side frame 16 and the left rear frames 13 face each other in the leftward/rightward direction (vehicle widthwise direction) and the right seatback side frame 16 and the right rear frames 13 face each other in the leftward/rightward direction (vehicle widthwise direction). The left rear frame 13 and the left seatback side frame 16 are connected to each other to be rotatable via a rotational connecting shaft (not shown). On the other hand, the right rear frame 13 and the right seatback side frame 16 are connected to each other via a seat reclining apparatus 25 to be rotatable about an axis extending in the leftward/rightward direction.

The seatback 12 (the seatback side frames 16) is rotatable about the aforementioned rotational connecting shaft and the seat reclining apparatus 25 relative to the seat cushion 11 (the rear frames 13). Specifically, the seatback 12 (the seatback side frames 16) is rotatable between a forwardly-tilted position shown by a two-dot chain line designated by 12A in FIG. 1 and a rearward-tilted position shown by a solid line designated by 12B in FIG. 1.

The detailed structure of the seat reclining apparatus 25 will be discussed hereinafter.

The seat reclining apparatus 25 is provided with the base plate 27, two lock members (pawls) 36, a lock member (pawl) 37, a wedge (second cam) 41, a rotational cam 47, a rotational center shaft 51, a ratchet plate 57, a retaining ring 64, a lock spring 68 and a spring cover 72, which are major elements of the seat reclining apparatus 25.

The base plate 27 is a metal disk member which is formed by press molding. The base plate 27 is provided on the outer edge of the left side thereof with a projecting large-diameter annular flange 28. The base plate 27 is provided with an accommodation space radially inside of the large-diameter annular flange 28. The base plate 27 is provided at a center thereof with a bearing hole 29 formed as a through-hole which is circular in cross sectional shape. The base plate 27 is provided on the left side thereof with three groove-forming projections 30 (see FIGS. 21 through 24) which project and are arranged at intervals of 120 degrees about the bearing hole 29. Each groove-forming projection 30 is substantially in the shape of a sector. The three groove-forming projections 30 are formed by pressing the right side of the base plate 27 leftward using a mold when the base plate 27 is formed by press molding. As shown in the drawings, a circular-arc-shaped clearance is formed between the outer periphery of each groove-forming projection 30 and the large-diameter annular flange 28. Both side surfaces of each groove-forming projection 30 (with respect to the circumferential direction of the base plate 27) are formed as flat guide surfaces 30 a, and the flat guide surfaces 30 a (opposed surfaces) of any two adjacent groove-forming projections 30 (which face each other in the circumferential direction) are parallel to each other, and a guide groove 31 is formed therebetween. The base plate 27 is further provided, on the right side thereof on the opposite sides from the three guide grooves 31, with a total of three welding protrusions 33 (see FIGS. 2, 4, 6, etc.), respectively, which project rightward. The three welding protrusions 33 are formed by pressing the bottoms (left side surfaces) of the three guide grooves 31 rightward by a mold when the base plate 27 is formed by press molding. The base plate 27 is further provided at the bases of the three guide grooves 31 with three protrusion-corresponding recesses 32 which are formed by the mold (which presses left side surfaces the bases of the three guide grooves 31) on the opposite sides from the three welding protrusions 33, respectively (see FIGS. 8, 9, 10, 12 and 13). Each welding protrusion 33 is substantially rectangular in shape, and both end surfaces of each welding protrusion 33 in the lengthwise direction thereof are formed as side end surfaces 33 a which are flat surfaces parallel to each other. In addition, a retaining projection 34 is formed on a center portion of the inner periphery of each welding protrusion 33 to project slightly toward the center of the base plate 27 (toward the inner peripheral side). The base plate 27 is further provided, on the right side thereof in the vicinity of the front welding protrusion 33 (the right welding protrusion 33 with respect to FIG. 13), with a pair of lock projections 35 which project rightward (see FIGS. 2, 13 and 14).

The two lock members 36 are installed in two of the three guide grooves 31, specifically in the front guide groove 31 (the left guide groove 31 with respect to FIG. 21) and the rear guide groove 31 (the right guide groove 31 with respect to FIG. 21), and the lock member 37 and the wedge 41 are installed in the upper guide groove 31 (the upper guide groove 31 with respect to FIG. 21).

The two lock members 36 and the lock member 37 are press-molded products made of metal plates, and the thicknesses of the three lock members 36 and 37 are substantially the same as the depths of the three guide grooves 31. A cam groove 38 is formed in each of the three lock members 36 and 37, while a wedge-engaging groove 39 is formed only in the lock member 37. As shown in FIG. 24, the wedge-engaging groove 39 is provided with a circumferential parallel portion 39 b, which extends substantially parallel to the circumferential direction about the axis of the base plate 27, and a pressed portion (pressure-receiving portion/abutment portion) 39 a, which extends obliquely toward the inner peripheral side from one end (the right end with respect to FIG. 24) of the circumferential parallel portion 39 b. The pressed portion 39 a is not linear (flat) in shape, but rather is a curved surface which is convex toward the space formed by the wedge-engaging groove 39 (toward the wedge 41; toward the left down side with respect to FIG. 24) (however, the curvature of the pressed portion 39 a is extremely small, so that the pressed portion 39 a appears to be substantially straight to the naked eye). The two lock members 36 and the lock member 37 are each provided on the circular-arc-shaped outer peripheral surface thereof with an outer toothed portion 40. In addition, the right side surfaces of each lock member 36 and 37 are flat surfaces. Additionally, each lock member 36 and 37 is provided on the left side thereof with an engaging projection 40 a which projects leftward and has a substantially rectangular cross sectional shape.

The wedge 41, which can be installed in the space formed by the wedge-engaging groove 39 of the wedge-engaging groove of the lock member 37, is a press-molded product made of a metal plate. The wedge 41 has smaller outside dimensions than the two lock members 36 and the lock member 37 and has substantially the same thickness as that of the two lock members 36 and the lock member 37.

The wedge 41 is symmetrical in shape with respect to a straight line L1 as shown in FIG. 25, and both the left and right sides of the wedge 41 lie flat on parallel planes. The wedge 41 is provided on the periphery thereof with an engaging portion 43, a pressing portion 44 and a slide-contact flat surface (surface contact portion) 45. The straight line L1 passes between the pressing portion 44 and the slide-contact flat surface 45. The peripheral surface of the engaging portion 43 is a circular arc surface which corresponds to a portion of an imaginary cylindrical surface 42 (the straight line L1 passing through the central axis thereof) positioned inside the wedge 41. The aforementioned curvature of the pressed portion 39 a of the lock member 37 is smaller than the curvature of the engaging portion 43 of the wedge 41. The pressing portion 44 and the slide-contact flat surface 45 of the wedge 41, which are formed to be symmetrical with respect to the straight line L1, are positioned outside the imaginary cylindrical surface 42 and are each formed from a flat surface inclined to the straight line L1. The wedge 41 is further provided with a clearance-forming portion 46 which is positioned on the engaging portion 43 side (the lower side with respect to FIG. 25) of a straight line L2 which is orthogonal to the straight line L1 and passes through the axis of the imaginary cylindrical surface 42. The clearance-forming portion 46 is formed of a portion of the wedge 41 which is positioned on the engaging portion 43 side of a straight line L2 and positioned outside the imaginary cylindrical surface 42 (specifically on the right-hand side of the imaginary cylindrical surface 42 with respect to FIG. 25). A concave surface 46 a (concave toward the inside of the wedge 41) which is continuous with the engaging portion 43 is formed on a peripheral surface of the clearance-forming portion 46.

The lock members 36, the lock member 37 and the wedge 41 are provided in the respective guide grooves 31 as shown in FIGS. 21 through 23. The right side surfaces of the lock members 36, the lock member 37 and the wedge 41 are all in surface contact with base (flat) surfaces (left side surfaces) of the guide grooves 31, respectively.

The rotational cam 47 is a press-molded product made of a metal plate and substantially identical in thickness to the three guide grooves 31. The rotational cam 47 is provided in the center thereof with a non-circular center hole 48, which is formed as a through-hole that is shaped as a circle with linearly cut-off opposite sides. The rotational cam 47 is provided, on the outer periphery thereof at intervals of 120 degrees, with three cam projections 49. As shown in the drawings, the rotational cam 47 is installed in the center of the aforementioned accommodation space of the base plate 27. As shown in FIG. 20, etc., the rotational cam 47 is provided, on the left side thereof at equi-angular intervals in the circumferential direction, with three rotation retaining projections 47 a which project leftward. The three rotation retaining projections 47 a are columnar in shape and mutually identical in specification. As shown in FIGS. 20 and 24, the rotational cam 47 is provided on the outer peripheries of the three cam projections 49 with three curved pressing surfaces 50, respectively, which are convex toward the outer peripheral side. The rotational cam 47 is further provided, on the outer periphery thereof at equi-angular intervals at different positions from the three curved pressing surfaces 50, with three lock-member pressing portions 47 b.

The rotational center shaft 51 is made of metal and provided with a cam connecting shaft 52 and an annular flange 54.

The cam connecting shaft 52 is a tubular member having a non-circular cross section. Both ends of the cam connecting shaft 52 are open as clearly shown in FIG. 19. The cam connecting shaft 52 is geometrically similar in cross sectional shape to and slightly smaller in size than the non-circular center hole 48. The cam connecting shaft 52 is provided therein with a connecting hole 53 which is also geometrically similar in cross sectional shape to the non-circular center hole 48.

The annular flange 54 is integrally formed on the rotational center shaft 51 to project radially outwards from the left end of the cam connecting shaft 52. The annular flange 54 is in the shape of a flat plate orthogonal to the axis of the cam connecting shaft 52.

In addition, the annular flange 54 is provided at equi-angular intervals in the circumferential direction thereof with a total of six through-holes: a pair of small-diameter circular holes 55 a, a pair of large-diameter through-holes 55 b and a pair of elongated holes 55 c. The pair of small-diameter circular holes 55 a are circular holes identical in diameter to the three rotation retaining projections 47 a. The pair of large-diameter through-holes 55 b are circular holes slightly greater in diameter than the pair of small-diameter circular holes 55 a (the rotation retaining projections 47 a). The pair of elongated holes 55 c are elongated holes which are shaped such that the minor diameter of each elongated hole 55 c is identical to the diameter of each small-diameter circular hole 55 a (each retaining projection 47 a) and that the major diameter of each elongated hole 55 c is greater than the diameter of each small-diameter circular hole 55 a (each retaining projection 47 a).

The rotational center shaft 51 is fixed to the rotational cam 47 with the two lock members 36, the lock member 37, the wedge 41 and the rotational cam 47 arranged in a clearance between the annular flange 54 and the base plate 27 and with the three rotation retaining projections 47 a of the rotational cam 47 respectively engaged in one of the pair of small-diameter circular holes 55 a, one of the pair of large-diameter through-holes 55 b and one of the pair of elongated holes 55 c. The cam connecting shaft 52 is loosely fitted into the non-circular center hole 48 of the rotational cam 47, and the end (right end) of the cam connecting shaft 52 projects rightward from the right side of the base plate 27 (see FIGS. 8 through 10). When the three rotation retaining projections 47 a are engaged in one small-diameter circular hole 55 a, one large-diameter through-hole 55 b and one elongated hole 55 c, respectively, play between the three rotation retaining projections 47 a and the one small-diameter circular hole 55 a, the one large-diameter through-hole 55 b and the one elongated hole 55 c substantially disappears, so that the rotational cam 47 and the rotational center shaft 51 become integral with each other (in other words, the rotational cam 47 and the rotational center shaft 51 are prevented from rotating relative to each other). Therefore, rotating the rotational center shaft 51 on the axis thereof relative to the base plate 27 (to the bearing hole 29) causes the rotational cam 47 to rotate with the rotational center shaft 51. In addition, since all the through-holes formed in the annular flange 54 are not formed as the small-diameter circular holes 55 a but are formed in the above described manner, the three rotation retaining projections 47 a can be easily fitted into three holes (one of the pair of small-diameter circular holes 55 a, one of the pair of large-diameter through-holes 55 b and one of the pair of elongated holes 55 c) formed in the annular flange 54.

The ratchet plate 57 is a press-molded metal product which is shaped into a disk. The ratchet plate 57 is provided on the outer edge of the right side thereof with a small-diameter annular flange 58 having a circular shape, so that an accommodation space is formed radially inside the small-diameter annular flange 58 on the right side of the ratchet plate 57. The ratchet plate 57 is provided at the center thereof with a bearing hole 59 formed as a through-hole which is circular in cross sectional shape. The ratchet plate 57 is provided, on the left side thereof at intervals of 90 degrees in the circumferential direction about the bearing hole 59, with a total of four welding protrusions 60 which project leftward. The ratchet plate 57 is provided on the outer edge of the left side thereof with an annular stepped portion 62 (see FIGS. 8 through 10) that is positioned in the back of the small-diameter annular flange 58. In addition, the ratchet plate 57 is provided on an inner peripheral surface of the small-diameter annular flange 58 with an internal gear 63. The ratchet plate 57 is further provided, at equi-angular intervals in the circumferential direction thereof on an inner peripheral surface of the small-diameter annular flange 58 which is positioned one step to the left of the internal gear 63, with three unlocked-state holding projections 57 a which project toward the inner peripheral side (see FIGS. 2 and 21 through 23). As shown in the drawings, the inner periphery of each unlocked-state holding projection 57 a is in the shape of a circular arc, the curvature center of which corresponds to the axis of the ratchet plate 57. The ratchet plate 57 is installed to cover the left side of the base plate 27 with the small-diameter annular flange 58 inserted into a clearance between the inner periphery of the large-diameter annular flange 28 and the outer peripheries of the three groove-forming projections 30. When the ratchet plate 57 is made to cover the base plate 27, the left side of the annular flange 54 faces the bottom (right side) of the aforementioned accommodation space of the ratchet plate 57 with a clearance formed therebetween, which prevents the rotational center shaft 51 from tilting relative to the axial direction thereof and prevents the two lock members 36, the lock member 37, the wedge 41 and the rotational cam 47 from rattling in the aforementioned accommodation spaces of the base plate 27 and the ratchet plate 57 in the axial direction of the rotational center shaft 51.

The retaining ring 64 is an annular ring member made of metal. The retaining ring 64 has a slightly greater outer diameter than that of the base plate 27. The retaining ring 64 is provided at the left end thereof with an annular adjacent portion 65 which projects toward the inner peripheral side (see FIGS. 8 through 10). The retaining ring 64 is fitted on the outer edges of the base plate 27 and the ratchet plate 57 with the annular adjacent portion 65 positioned on (opposed to) the left side of the annular stepped portion 62. The retaining ring 64 is provided on the right end thereof with an annular swaging portion 66. The retaining ring 64 is fixed to the base plate 27 by swaging the annular swaging portion 66 against an annular recess formed on the perimeter of the right side of the base plate 27. Once the base plate 27 and the retaining ring 64 are integrated (fixed to each other), the ratchet plate 57 is positioned between the base plate 27 and the retaining ring 64 so that the ratchet plate 57 is rotatable relative to the base plate 27 and the retaining ring 64 about the rotational center shaft 51 without coming off the base plate 27 or the retaining plate 64.

The lock spring 68 is a spiral spring that is formed by winding a metal belt into a spiral and is installed on the right side of the base plate 27. The end (inner end) of the lock spring 68 on the inner peripheral side is formed as a first locking portion 69 that is formed by bending the inner end of the lock spring 68 into a linear shape. The end (outer end) of the lock spring 68 on the outer peripheral side is formed as a second locking portion 70 which extends in a direction substantially parallel to a radial direction of the lock spring 68.

The lock spring 68 is installed around the right end of the cam connecting shaft 52 that projects from the base plate 27. As shown in FIG. 14, the first locking portion 69 is locked onto a flat portion of the cam connecting shaft 52 which constitutes a portion of the outer periphery of the cam connecting shaft 52, while the second locking portion 70 is locked onto one of the locking projections 35.

When the lock spring 68 is installed onto the base plate 27 and the rotational center shaft 51 (the cam connecting shaft 52) in the above described manner, the lock spring 68 is slightly resiliently deformed to produce a biasing force that urges the rotational center shaft 51 to rotate in one direction. This biasing force urges the rotational center shaft 51 to rotate counterclockwise with respect to FIGS. 21 through 23, and accordingly, the rotational cam 47 is in the locked position shown in FIG. 21 when no external force other than the biasing force of the lock spring 68 is exerted on the rotational center shaft 51. When the rotational cam 47 is in the locked position, each lock-member pressing portion 47 b presses the associated lock member 36 or 37 in a locking direction (toward the outer peripheral side). In addition, the curved pressing surface 50 of the specific cam projection 49 (specifically the upper cam projection 49 with respect to FIG. 21; the cam projection 49 shown in FIG. 24) of the rotational cam 47 presses the engaging portion 43 of the wedge 41 in a locking direction (toward the outer peripheral side), so that the wedge 41 slides toward the outer peripheral side of the base plate 27 while being guided by the flat guide surface 30 a with which the slide-contact flat surface 45 of the wedge 41 is in surface contact, and the pressing portion 44 of the wedge 41 partly contacts and presses the pressed portion 39 a with a large force. Therefore, the lock member 37 which is pressed both toward the flat guide surface 30 a (which is positioned on the right-hand side of the lock member 37 with respect to FIG. 21) and in the locking direction moves to an engaged position in which the outer toothed portion 40 of the lock member 37 is engaged with internal gear 63 of the ratchet plate 57, so that the lock member 37 becomes immovable in the associated guide groove 31. On the other hand, since each of the two lock members 36 is allowed to move in a circumferential direction within a gap defined between the associated guide groove 31 and the associated lock member 36, each lock member 36 comes into engagement with the internal gear 63 of the ratchet plate 57 while moving (adjusting) in a circumferential direction within the gap defined between the associated guide groove 31 and the associated lock member 36. Accordingly, when the rotational cam 47 rotates to the locked position, each of the three lock members (the two lock members 36 and the lock member 37) securely performs a locking operation, so that the base plate 27 and the ratchet plate 57 are prevented from rotating relative to each other. In addition, the outer peripheral surfaces of the engaging projections 40 a of the three lock members 36 and 37 are positioned closer to the outer peripheral side than the inner peripheral surfaces of the three unlocked-state holding projections 57 a.

On the other hand, rotating the rotational center shaft 51 clockwise with respect to FIGS. 21 through 23 against the rotational biasing force of the lock spring 68 causes the rotational cam 47, which is in the locked position, to rotate to the unlocked position shown in FIG. 22. Thereupon, each of the three lock-member pressing portions 47 b is disengaged from the associated lock member 36 or 37 toward the inner peripheral side, thus causing the curved pressing surface 50 of the specific cam projection 49 (specifically, the upper cam projection 49 with respect to FIG. 21) of the rotational cam 47 to be disengaged in the circumferential direction from the engaging portion 43 of the wedge 41. Additionally, each cam projection 49 engages with the associated cam groove 38 to move the associated lock member 36 or 37 radially inwards to the disengaged position shown in FIG. 22, which causes the outer toothed portions 40 of the three lock members 36 and 37 and the internal gear 63 of the ratchet plate 57 to be disengaged from each other to thereby allow the base plate 27 and the ratchet plate 57 to rotate relative to each other. Additionally, the wedge 41 becomes freely movable in the associated guide groove 31 within the area surrounded by the associated flat guide surface 30 a, the lock member 37 (the pressed portion 39 a) and the rotational cam 47 (the associated cam projection 49). Additionally, the outer peripheral surfaces of the engaging projections 40 a of the three lock members 36 and 37 are positioned closer to the inner peripheral side than the inner peripheral surfaces of the three unlocked-state holding projections 57 a.

The spring cover 72 is made of metal and is mounted to the right side of the base plate 27. The spring cover 72 is formed from a metal plate by press molding. The base of the spring cover 72 includes a spring housing portion 73 which is non-circular in a side view and the entire left end surface thereof is open. A circular through-hole 74 is formed in the center of the spring housing portion 73. The spring cover 72 is provided on the outer edge of the left end of the spring housing portion 73 with an engaging projection 75, which is V-shaped in cross section and projects toward the outer peripheral side. In addition, the spring cover 72 is provided, on the outer edge of the left end of the spring housing portion 73 at different circumferential positions from the engaging projection 75, with two pressed lugs 76 which project toward the outer peripheral side. The two pressed lugs 76 are flat lugs which lie in a plane orthogonal to the leftward/rightward direction.

The spring cover 72 is installed onto the right side of the base plate 27 with the end of the cam connecting shaft 52 positioned in the circular through-hole 74 and with the spring housing portion 73 positioned between the three welding protrusions 33. Fitting the spring housing portion 73 into the space between the three welding protrusions 33 causes the retaining projections 34 of two of the three welding protrusions 33 to be engaged with two parts of the outer edge of the spring housing portion 73, respectively, and causes the retaining projection 34 of the remaining one welding protrusion 33 to be engaged with the end of the engaging projection 75. Accordingly, when the spring cover 72 is installed onto the right side of the base plate 27, the spring cover 72 becomes integral with the right side of the base plate 27.

As shown in FIG. 6, the base plate 27 of the seat reclining apparatus 25 is installed onto the rear frame 13 with the three welding protrusions 33 of the base plate 27 respectively engaged in the three engaging holes 15 of the rear frame 13 and with the side end surfaces 33 a of each welding protrusion 33 respectively being in surface contact with the pair of flat portions 15 a of the associated engaging hole 15. The rear frame 13 and the base plate 27 are fixed to each other by applying a weld W1 (indicated by many small cross marks shown in FIG. 11 and hatch lines shown in FIG. 12), from the right side of the rear frame 13, to each of three welding portions (only one of which is shown in FIG. 11) each of which extends over an outer peripheral edge (right edge with respect to FIG. 11) of one engaging hole 15 and an outer peripheral edge of the right end surface of the associated welding protrusion 33. As shown in FIG. 11, the outer peripheral edge of the right end surface of each welding protrusion 33 (the position at which the weld W1 is applied) is positioned closer to the outer peripheral side than the position of the internal gear 63 (i.e., the positions of the outer toothed portions 40 of the three lock members 36 and 37 when each of the three lock members 36 and 37 is in the engaged position) and the outer peripheral edges of the three protrusion-corresponding recesses 32 (see FIGS. 11 and 13). In addition, when the base plate 27 is fixed to the rear frame 13, an inner side surface of the rear frame 13 (the outer edge of the seat-cushion-side connecting hole 14) comes in contact with the outer side surfaces of the two pressed lugs 76, which easily and securely prevents the spring cover 72 from coming off the right side of the base plate 27.

On the other hand, the ratchet plate 57 of the seat reclining apparatus 25 is fixed to the seatback side frame 16 by respectively engaging the four welding protrusions 60 in the four fitting holes 18 and applying a weld (not shown), from the left side of the seatback side frame 16, to an outer peripheral edge of each engaging hole 18 and an outer peripheral edge of the left end surface of the associated welding protrusion 60.

After the rear frame 13 and the seatback side frame 16 are connected to the seat reclining apparatus 25, a connecting shaft (not shown) having a non-circular cross sectional shape which extends leftward from the base end of an operating lever (operating member) 21 (see FIG. 1) is press-fitted into the connecting hole 53 of the cam connecting shaft 52 through the circular through-hole 74 of the spring cover 72 to be fixed to the rotational center shaft 51 (to the connecting hole 53). Therefore, rotating the operating lever 21 about the aforementioned connecting shaft causes the rotational center shaft 51 to rotate with the operating lever 21 (the aforementioned connecting shaft).

Operations of the vehicle seat 10 will be discussed hereinafter.

When no external force is applied to the operating lever 21, the operating lever 21 is held in the non-operating position shown by a solid line in FIG. 1 by the rotational biasing force of the lock spring 68. Additionally, when no external force is applied to the operating lever 21, the rotational cam 47 is in the locked position and the lock member 37 is in the engaged position, so that the seat reclining apparatus 25 is in a locked state. This prevents the seat cushion 11 (the rear frame 13), which is integral with the base plate 27, and the seatback 12 (the pair of seatback side frames 16), which is integral with the ratchet plate 57, from rotating relative to each other. On the other hand, rotating the operating lever 21 counterclockwise with respect to FIG. 1 to the operating position shown by a two-dot chain line in FIG. 1 against the rotational biasing force of the lock spring 68 causes the rotational cam 47 to rotate to the unlocked position, thus causing each of the two lock members 36 and the lock member 37 to move to the disengaged position, so that the seat reclining apparatus 25 comes into an unlocked state. This allows the seat cushion 11 (the rear frame 13), which is integral with the base plate 27, and the seatback 12 (the pair of seatback side frames 16), which is integral with the ratchet plate 57, to rotate relative to each other.

When the seatback 12 (the pair of seatback side frames 16) is in a first-stage locked position shown by a solid line in FIG. 1, rotating the operating lever 21 to the operating position to move the seat reclining apparatus 25 to the unlocked state causes the seatback 12 to rotate (tilt) forward by the rotational biasing force of a rotational biasing spring (not shown) installed in the vehicle seat 10. Thereupon, since the ratchet plate 57 rotates counterclockwise with respect to FIGS. 21 through 23 relative to the base plate 27, the seat reclining apparatus 25 comes into an unlocked holding state (i.e., a state in which the seat reclining apparatus 25 is held in the unlocked state) in which the three engaging projections 40 a (the outer peripheral surface thereof) that are positioned closer to the inner peripheral side than the inner peripheral surfaces of the three unlocked-state holding projections 57 a radially oppose (face) (to be in contact with) the inner peripheral surfaces of the three unlocked-state holding projections 57 a, respectively, as shown in FIG. 23 (which shows a state of the interior of the seat reclining apparatus 25 when the seatback 12 has slightly rotated forward from the first-stage locked position). Therefore, the operating lever 21 is prevented from moving toward the non-operating position (the rotational cam 47 and the lock member 37 are also prevented from moving toward the locked position and the engaged position, respectively), so that the seatback 12 rotates to the aforementioned forwardly-tilted position (shown by a two-dot chain line designated by 12A in FIG. 1) by the rotational biasing force of the aforementioned rotational biasing spring. When the seatback 12 is positioned in between a position (shown in FIG. 23) slightly rotated forward from the first-stage locked position and the forward-tilted position (shown by a two-dot chain line designated by 12A in FIG. 1), the seat reclining apparatus 25 is held in the aforementioned unlocked holding state.

On the other hand, when the seatback 12 is positioned at or behind the first-stage locked position shown by a solid line in FIG. 1, if one rotates the operating lever 21 in the non-operating position to the operating position while applying a rearward force to the seatback 12 (e.g., by the back of an occupant sitting in the vehicle seat 10) to change the seat reclining apparatus 25 to an unlocked state, the seatback 12 rotates rearward. Subsequently, if one returns the operating lever 21 to the non-operating position upon tilting the seatback 12 to a desired rearward-tilted position, the rotational cam 47 moves back to the locked position while each lock member 36 and 37 moves back to the engaged position by the rotational biasing force of the lock spring 68, so that the seatback 12 (the pair of seatback side frames 16) is held at the desired tilted position.

The wedge 41 of the above described embodiment of the seat reclining apparatus 25 is provided with the slide-contact flat surface 45, which comes in surface contact with the adjacent flat guide surface 30 a of the associated groove-forming projection 30. Therefore, when the seat reclining apparatus 25 is in the locked state, even if forward or rearward loads are exerted on the seatback 12 to thereby cause the aforementioned adjacent flat guide surface 30 a and the slide-contact flat surface 45 to come into contact with each other with a large force due to, e.g., a vehicle which incorporates the seat reclining apparatus 25 colliding with another vehicle, concentrated loads do not easily occur between the aforementioned adjacent flat guide surface 30 a (the associated groove-forming projection 30) and the wedge 41.

In addition, since the pressed portion 39 a of the lock member 37 is a curved surface that is convex toward the wedge 41 though the pressing portion 44 of the wedge 41 is flat in shape, even if an error exits between the shape of the wedge 41 (the pressing portion 44) and the design shape thereof, there is little possibility of the wedge 41 becoming positionally unstable when the rotational cam 47 rotates, so that the operation of the wedge 41 does not easily become unsmooth.

Additionally, since the press portion 39 a of the lock member 37 has a profile that is close to that of the pressing portion 44 of the wedge 41 (has a curved profile that is close to a flat surface), the wedge 41 (the pressing portion 44) or the lock member 37 (the pressed portion 39) easily deforms plastically into the same shape as the pressed portion 39 a of the lock member 37 or the pressing portion 44 of the wedge 41, respectively, when the pressing portion 44 of the wedge 41 and the pressed portion 39 a of the lock member 37 come into contact with each other with a large force due to, e.g., a vehicle which incorporates the seat reclining apparatus 25 colliding with another vehicle. If one of the pressing portion 44 of the wedge 41 and the pressed portion 39 a of the lock member 37 becomes deformed into the same shape as the other, the contact state between the pressing portion 44 of the wedge 41 and the pressed portion 39 a of the lock member 37 becomes a surface contact state, which reduces the possibility of large concentrated loads occurring therebetween. Accordingly, one or both of the wedge 41 and the lock member 37 can be efficiently prevented from being deformed or damaged.

In addition, the seat reclining apparatus 25 has only one wedge (the wedge 41) while having more than one lock member (the two lock members 36 and the lock member 37). Therefore, when the outer toothed portion 40 of the lock member 37 which is pressed in the locking direction by the wedge 41 is engaged with the internal gear 63 of the ratchet plate 57, the positions of the lock member 37 and the ratchet plate 57 are fixed (a positional reference is determined), and the lock member 37 becomes immovable in the associated guide groove 31. On the other hand, each of the remaining two lock members 36 is allowed to move in a circumferential direction within the gap defined between the associated guide groove 31 and the associated lock member 36, thus being engaged with the internal gear 63 of the ratchet plate 57 while moving, as appropriate, in a circumferential direction within the gap defined between the associated guide groove 31 and the associated lock member 36. Accordingly, since all the three lock members, i.e., the two lock members 36 and the lock member 37, operate with reliability when the rotational cam 47 rotates, the seat reclining apparatus 25 can reliably perform locking and unlocking operations.

Additionally, when the seat reclining apparatus 25 comes into the locked state, the wedge 41 comes into contact with the following three members: the rotational cam 47, the lock member 37 and the base plate 27 (the adjacent flat guide surface 30 a of the associated groove-forming projection 30), so that the behavior of the wedge 41 is appropriately controlled.

Additionally, the wedge 41 has the concave surface 46 a that forms a clearance between the wedge 41 and the associated curved pressing surface 50 of the rotational cam 47 when facing the associated curved pressing surface 50 of the rotational cam 47 as shown in FIG. 24. The concave surface 46 a is a concave surface which faces a protrusion constituting the associated curved pressing surface 50 and has a shape capable of approaching the associated curved pressing surface 50, and accordingly, the clearance between the associated curved pressing surface 50 of the rotational cam 47 and the concave surface 46 a when the rotational cam 47 is in the unlocked position is narrow.

If an occupant pushes the seatback 12 rearward or forward when the seat reclining apparatus 25 is in the locked state, a force in the circumferential direction of the base plate 27 is exerted on the outer toothed portion 40 of each of the two lock members 36 and the lock member 37 from the internal gear 63 of the ratchet plate 57, and a component of this force which is directed toward the inner peripheral side becomes a force urging the two lock members 36, the lock member 37 and the wedge 41 toward the inner peripheral side (toward the rotational cam 47 side).

In this state, upon an occupant unlocking the seat reclining apparatus 25, the curved pressing surface 50 of the rotational cam 47 moves away from the wedge 41 in the circumferential direction of the rotational cam 47 (the base plate 27). Thereupon, the wedge 41 which receives the aforementioned component of force (which is directed toward the inner peripheral side) moves toward the rotational cam 47. However, since the clearance between the concave surface 46 a of the wedge 41 and the associated curved pressing surface 50 of the rotational cam 47 is narrow (the distance therebetween is small) as mentioned above, a high collision speed of the wedge 41 against the rotational cam 47 does not easily occur even if the concave surface 46 a of the wedge 41 collides with the associated curved pressing surface 50 of the rotational cam 47, so that the possibility of a loud sound (noise) of such a collision being produced between the wedge 41 (the concave surface 46 a) and the rotational cam 47 (the associated curved pressing surface 50) is small.

Additionally, the pair of small-diameter circular holes 55 a, the pair of large-diameter through-holes 55 b and the pair of elongated holes 55 c are formed in the annular flange 54 that rotates with the rotational center shaft 51, and the three rotation retaining projections 47 a are projected from the rotational cam 47 to be engaged in one of the pair of small-diameter circular holes 55 a, one of the pair of large-diameter through-holes 55 b and one of the pair of elongated holes 55 c, respectively. Therefore, when the rotational center shaft 51 rotates, this rotational operating force is transmitted to the three rotation retaining projections 47 a via the one of the pair of small-diameter circular holes 55 a, the one of the pair of large-diameter through-holes 55 b and the one of the pair of elongated holes 55 c that are formed in the annular flange 54. The magnitude of the force transmitted from the rotational center shaft 51 (the annular flange 54) to the rotational cam 47 is equal to the magnitude of the rotation moment (torque) of the rotational center shaft 51 (the annular flange 54) divided by the direct distance (distance in a radial direction of the annular flange 54) from the axis of the rotational center shaft 51 to the one of the pair of small-diameter circular holes 55 a, the one of the pair of large-diameter through-holes 55 b or the one of the pair of elongated holes 55 c. Since the pair of small-diameter circular holes 55 a, the pair of large-diameter through-holes 55 b and the pair of elongated holes 55 c, which are formed in the annular flange 54, are positioned closer to the outer peripheral side than the cam connecting shaft 52 (the non-circular center hole 48 of the rotational cam 47), the aforementioned direct distance is longer than the radius of the cam connecting shaft 52 (the radius of the non-circular center hole 48 of the rotational cam 47). Therefore, the force transmitted from the rotational center shaft 51 (the annular flange 54) to the rotational cam 47 does not become too large. Accordingly, even if a force urging the operating lever 21 to rotate beyond a predetermined normal range of rotation is produced (even if a force urging the operating lever 21 to rotate in the direction reverse to the operating position beyond the non-operating position or in the direction reverse to the non-operating position beyond the operating position is produced) as a result of, e.g., a foot of an occupant accidentally coming into contact with the operating lever 21, the possibility of the rotational cam 47 or the rotational center shaft 51 (the annular flange 54) being deformed is small.

Additionally, the three welding portions (to each of which the weld W1 has been applied), which are formed on outer peripheral portions of the three welding protrusions 33 that are projected from the base plate 27, are positioned closer to the outer peripheral side than the outer toothed portions 40 of the three lock members 36 and 37 which are positioned in the engaged position. Therefore, the possibility of heat of the weld W1 reaching and deforming a portion of the bottom of each of the three guide groove 31 on which the associated lock member 36 or 37 slides (e.g., deforming this portion so that it protrudes toward the associated lock member 36 or 37) is small. Additionally, even if heat of the weld W1 reaching each of the three protrusion-corresponding recesses 32, which are respectively positioned directly behind the three welding protrusions 33, and the inner surfaces of the three protrusion-corresponding recesses 32 are deformed by this heat, this deformation has no effect on the operation of each lock member 36 and 37 because the inner surfaces of the three protrusion-corresponding recesses 32 are spaced from the three lock members 36 and 37. Accordingly, the possibility of each lock member 36 and 37 becoming incapable of sliding on an inner side surface (the associated guide groove 31) of the base plate 27 due to heat of the weld W1 is small.

Additionally, since the pair of side end surfaces 33 a of each welding protrusion 33 are in surface contact with the pair of flat portions 15 a of the associated engaging hole 15, it is possible to secure a large contact area between each welding protrusion 33 (the pair of side end surfaces 33 a) and the associated engaging hole 15 (the pair of flat portions 15 a). Accordingly, even if a collision load occurs between the pair of side end surfaces 33 a of each welding protrusion 33 and the pair of flat portions 15 a of the associated engaging hole 15 due to, e.g., a vehicle which incorporates the seat reclining apparatus 25 colliding with another vehicle, the seat reclining apparatus 25 can exhibit high resistance to this collision load.

Although the present invention has been described based on the above illustrated embodiment of the seat reclining apparatus, the present invention is not limited solely to this particular embodiment; various modifications to the above illustrated embodiment of the seat reclining apparatus are possible.

For instance, it is possible to fix the base plate 27 to the pair of seatback side frames 16 and fix the ratchet plate 57 to the rear frame 13.

In addition, the left rear frame 13 (the left seat cushion frame) and the left seatback side frame 16 can be connected to each other via the seat reclining apparatus 25 instead of the right rear frame 13 (the right seat cushion frame) and the right seatback side frame 16 being connected to each other via the seat reclining apparatus 25. Additionally, it is possible to connect the left and right rear frames 13 and the left and right seatback side frames 16 to each other via left and right seat reclining apparatuses 25, respectively, and connect the rotational center shafts 51 of the left and right seat reclining apparatuses 25 to each other via a connecting pipe, or the like, so that the left and right seat reclining apparatuses 25 move in synchronization with each other.

Since the wedge 41 is symmetrical in shape with respect to the straight line L1 as shown in FIG. 25, the wedge 41 can also be applied to the left seat reclining apparatus 25 in the case where the seat reclining apparatus 25 is installed to each of the left and right sides of the vehicle seat 10 (or in the case where the seat reclining apparatus 25 is installed only onto the left side of the vehicle seat 10).

Additionally, it is possible to form the pressed portion 39 a of the lock member 37 into a linear (flat) shape and form the pressing portion 44 of the wedge 41 into a curved surface (corresponding to the curved surface of the pressed portion 39 a in the above described embodiment, which is smaller in curvature than the engaging portion 43 of the wedge 41) which is convex toward the pressed portion 39 a.

Additionally, as shown in FIG. 26, the lock member 37 and the wedge 41 can be replaced by an integral-type lock member 37′, the shape of which corresponds to the shape of an integral combination of the lock member 37 and the wedge 41 (note that a two-dot chain line shown in FIG. 26 shows a contour line of a portion of the integral-type lock member 37′ which corresponds to the wedge 41).

The seat reclining apparatus according to the present invention can be provided with a plurality of wedges, each of which corresponds to the wedge 41, and a plurality of lock members (each of which has the wedge-engaging groove 39) can be pressed by the plurality of wedges. In this case, the number of the plurality of wedges can be equal to or less than the number of the plurality of lock members.

Additionally, the curved pressing surface 50 of the rotational cam 47 is not required to be a curved surface so long as it is formed into a shape that is convex toward the concave surface 46 a of the wedge 41; on the other hand, the concave surface 46 a of the wedge 41 is also not required to be a curved surface so long as it is formed into a shape that is concave toward the opposite side from the associated curved pressing surface 50 of the rotational cam 47.

Additionally, it is possible for the rotational center shaft 51 to be provided, on the annular flange 54 side thereof, with rotation retaining projections corresponding to the rotation retaining projections 47 a and for the rotational cam 47 to be provided with a small-diameter circular hole(s), a large-diameter through-hole(s) and an elongated hole(s) corresponding to the small-diameter circular hole(s) 55 a, the large-diameter through-hole(s) 55 b and the elongated hole(s) 55 c, respectively.

Additionally, the number of rotation retaining projections 47 a and the number of holes 55 a, 55 b and 55 c can each be one in either case where rotation retaining projections corresponding to the three rotation retaining projections 47 a and holes corresponding to the holes 55 a, 55 b and holes 55 c are formed on the rotational cam 47 and the rotational center shaft 51 or the rotational center shaft 51 and the rotational cam 47, respectively.

Additionally, the three engaging holes 15 of the rear frame 13 can be formed as bottomed holes, the ends of which on the opposite side of the rear frame 13 from the base plate 27 side are closed, rather than as through-holes.

Additionally, the three protrusion-corresponding recesses 32 can be omitted from the base plate 27 by, e.g., forming the base plate 27 by forging.

Additionally, a through-hole (as a substitution for the bearing hole 29) greater in diameter than the bearing hole 29 can be formed in the center of the base plate 27 to install the lock spring 68 in this through-hole (within the plate thickness of the base plate 27).

Additionally, the lock spring 68 and the spring cover 72 can be installed onto the left side of the ratchet plate 57, or a through-hole (as a substitution for the bearing hole 59) greater in diameter than the bearing hole 59 can be formed in the center of the ratchet plate 57 to install the lock spring 68 (which is installed onto the left side of the ratchet plate 57) in this through-hole (within the plate thickness of the ratchet plate 57). In this case, the inner side of the seatback side frame 16 (the edge of the seatback-side connecting hole 17), that is shown by two-dot chain lines in FIG. 2, is made to contact the outer peripheries of the two pressed lugs 76.

The seat reclining apparatus 25 can be modified to be a so-called swing-pawl type in which each lock member (pawl) is allowed to move not only linearly in a radial direction of the base plate 27 relative to the base plate 27 but also in a radial direction of the base plate 27 while swinging relative to the base plate 27.

In this case, the circumferentially opposite surfaces of each lock member 36 and 37 that respectively face the flat guide surfaces 30 a in the associated guide groove 31 can be formed as flat surfaces, or the flat guide surfaces 30 a can be replaced by curved guide surfaces while the circumferentially opposite surfaces of each lock member that respectively face the aforementioned curved guide surfaces 30 a can be formed as curved surfaces (surface contact portions) which can be in surface contact with the aforementioned curved guide surfaces 30 a.

The seat reclining apparatus 25 can be modified into a so-called release type that incorporates a release plate which is linked with the rotational cam 47 and the three lock members 36 and 37 instead of omitting the three cam projections 49 from the rotational cam 47.

Additionally, the number of the welding protrusions 33 is not limited to three.

Furthermore, the aforementioned connecting shaft (not shown) of the operating lever 21 can be retained so as not to come off the connecting hole 53 by installing a push nut onto the end of the connecting shaft after the connecting shaft is inserted into the connecting hole 53.

Obvious changes may be made in the specific embodiment of the present invention described herein, such modifications being within the spirit and scope of the invention claimed. It is indicated that all matter contained herein is illustrative and does not limit the scope of the present invention. 

What is claimed is:
 1. A seat reclining apparatus comprising: a base plate which is fixed to one of a seat cushion side frame and a seatback side frame; a ratchet plate which includes an internal gear, said ratchet plate being fixed to the other of said seat cushion side frame and said seatback side frame so as to face said base plate while being rotatable relative thereto; a guide groove which is formed on a surface of said base plate which faces said ratchet plate; a lock member guided by said guide groove so as to be movable between an engaged position, in which an outer toothed portion formed on an outer peripheral surface of said lock member is engaged with said internal gear of said ratchet plate, and a disengaged position, in which said outer toothed portion is disengaged from said internal gear of said ratchet plate toward an inner peripheral side; a first cam which is positioned between said base plate and said ratchet plate and rotates relative to said base plate and said ratchet plate in association with an operation of operating member between a locked position to position said lock member in said engaged position and an unlocked position to position said lock member in said disengaged position; and a second cam which moves toward said lock member and presses said lock member to said engaged position by receiving a force from said first cam when said first cam rotates from said unlocked position to said locked position, wherein said second cam includes a surface contact portion which comes in surface contact with a guide surface in said guide groove, an engaging portion which is pressed by said first cam, and a pressing portion which presses a pressed portion of said lock member, and wherein one of said pressing portion of said second cam and said pressed portion of said lock member includes a flat surface, and the other of said pressing portion of said second cam and said pressed portion of said lock member includes a curved surface that is convex toward said flat surface.
 2. The seat reclining apparatus according to claim 1, wherein said engaging portion of said second cam comprises a curved surface that is convex toward said first cam, and wherein the curvature of said curved surface of said engaging portion of said second cam is greater than the curvature of said curved surface of said other of said pressing portion of said second cam and said pressed portion of said lock member.
 3. The seat reclining apparatus according to claim 1, wherein said pressing portion of said second cam and said pressed portion of said lock member comprise said flat surface and said curved surface, respectively, wherein said surface contact portion of said second cam comprises a flat surface; and wherein said second cam is symmetrical in shape with respect to a straight line passing between said surface contact portion and said pressing portion.
 4. The seat reclining apparatus according to claim 1, wherein said guide groove comprises a plurality of guide grooves, wherein said lock member comprises a plurality of lock members which are guided by said plurality of guide grooves, respectively, and wherein said second cam operates in association with one of said plurality of lock members. 